CN217876540U

CN217876540U - Air supplementing system of heat pump all-in-one machine

Info

Publication number: CN217876540U
Application number: CN202221557144.3U
Authority: CN
Inventors: 李福辉; 五十住晋一; 相金波
Original assignee: Mitsubishi Heavy Industries Haier Qingdao Air Conditioners Co Ltd
Current assignee: Mitsubishi Heavy Industries Haier Qingdao Air Conditioners Co Ltd
Priority date: 2022-06-21
Filing date: 2022-06-21
Publication date: 2022-11-22
Anticipated expiration: 2032-06-21

Abstract

The utility model discloses a heat pump all-in-one air supplement system, which comprises a compressor, three control reservoirs, first heat exchanger, the second heat exchanger, four-way reversing valve, the check valve, first expansion valve, the second expansion valve, first temperature sensor and second temperature sensor, three control reservoirs connect water heat exchanger respectively, wind heat exchanger and compressor, first expansion valve sets up between three control reservoirs and first heat exchanger, the second expansion valve sets up between three control reservoirs and second heat exchanger, water heat exchanger is connected respectively to the four-way valve, wind heat exchanger, compressor and check valve, the compressor is still connected to the check valve. The utility model discloses a heat pump all-in-one air make-up system has improved air conditioning unit's performance, has optimized the operating stability of unit under extreme operating mode.

Description

Air supplementing system of heat pump all-in-one machine

Technical Field

The utility model relates to an air conditioner technical field, in particular to heat pump all-in-one tonifying qi system.

Background

At present, in the central air-conditioning industry of China, R410a refrigerant is commonly used, the technology is mature, but due to the high GWP characteristic, in developed areas such as Europe, air conditioners taking the R410a refrigerant as a working medium are forbidden to be sold, and due to the fact that the R32 refrigerant has the low GWP characteristic, the high heat exchange efficiency and the low refrigerant charge, compared with the R410a refrigerant, the refrigerant has a wide application prospect, is favored by a plurality of central air-conditioning manufacturers, and a plurality of manufacturers start to gradually switch from the R410a refrigerant to the R32 refrigerant.

However, due to the characteristic that the operating pressure and the exhaust temperature of the R32 refrigerant are high, the air conditioner is likely to give an alarm under high pressure, give an alarm under overhigh exhaust temperature, limit frequency and reduce frequency in the operating process, the full potential of the unit cannot be exerted, and the most direct feeling brought to a user is that the air conditioner operates without strength, so that the adverse effect is caused to the public praise of an air conditioner manufacturer.

In the prior art, generally, the compressor is changed into an enhanced vapor injection compressor, the capacity and the energy efficiency of the air source heat pump unit are improved, the operation range of the unit can be effectively widened, and the air source heat pump unit has the following defects: an additional economizer is generally needed, and the cost is increased; in addition, the economizer needs to be additionally arranged in the unit in a searching mode, occupies the internal space of the unit, increases the design size of the unit, increases the cost and the like.

SUMMERY OF THE UTILITY MODEL

The utility model provides a heat pump all-in-one air supplement system to R32 refrigerant operating pressure, exhaust temperature are all high among the solution prior art, influence the problem of air conditioner normal use.

In order to solve the technical problem, the utility model discloses a technical scheme does:

the utility model provides a heat pump all-in-one tonifying qi system, includes: a compressor including an exhaust port, an intake port, and a supply port;

the four-way reversing valve comprises a first valve port, a second valve port, a third valve port and a fourth valve port, the first valve port is connected with the exhaust port through a first pipeline, the second valve port is connected with the first heat exchanger through a second pipeline, the third valve port is connected with the second heat exchanger through a third pipeline, and the fourth valve port is connected with the air suction port through a fourth pipeline; when the system heats, the first valve port is communicated with the second valve port, the third valve port is communicated with the fourth valve port, and when the system cools, the first valve port is communicated with the third valve port, and the second valve port is communicated with the fourth valve port;

a check valve disposed on the first pipeline; and

the liquid in the three-pipe liquid storage device enters and exits through the first exchange port and the second exchange port, and the gas in the three-pipe liquid storage device enters and exits through the gas outlet;

the gas outlet is connected with the gas supplementing port through a fifth pipeline, the first exchange port is connected with the first heat exchanger through a sixth pipeline, the second exchange port is connected with the second heat exchanger through a seventh pipeline, the fifth pipeline is provided with a first temperature sensor, the sixth pipeline is provided with a first expansion valve and a second temperature sensor, and the seventh pipeline is provided with a second expansion valve.

Furthermore, a control valve is further arranged on the fifth pipeline.

Further: the first expansion valve and the second expansion valve are both electronic expansion valves.

And further: the control valve is an electromagnetic valve.

And further: the compressor is an enhanced vapor injection compressor.

By adopting the technical scheme, an economizer is not required to be added, and only a copper pipe is led out on the basis of the traditional liquid storage device and connected to the air supplement port of the EVI compressor, so that air supplement of the compressor can be realized, the flow of a refrigerant is increased, the exhaust temperature of the compressor is reduced, the exhaust temperature of the compressor does not exceed the standard under extreme working conditions such as high-temperature refrigeration and low-temperature heating, and the operation range of the air source heat pump unit is widened. Meanwhile, the three-pipe liquid storage device has a flash evaporation function, liquid in the tank can be supercooled, cold media after cold are throttled and enter heat exchange to be evaporated and absorbed, and the heat pump unit can obtain higher capacity and energy efficiency due to the larger heat exchange temperature difference.

Drawings

FIG. 1 is a schematic structural view of the air make-up system of the heat pump all-in-one machine of the present invention;

in the figure, 1-EVI compressor, 2-four-way reversing valve, 3-water heat exchanger, 4-three-pipe liquid storage device, 5-air heat exchanger, 61-first pipeline, 62-second pipeline, 63-third pipeline, 64-fourth pipeline, 65-fifth pipeline, 66-sixth pipeline, 67-seventh pipeline, 71-first temperature sensor, 72-second temperature sensor, 73-third temperature sensor, 74-fourth temperature sensor, 81-one-way valve, 82-first electronic expansion valve, 83-second electronic expansion valve, 84-solenoid valve, 91-first pressure sensor, 92-second pressure sensor and 93-pressure switch.

Detailed Description

The following describes the present invention with reference to the accompanying drawings. It should be noted that the description of the embodiments is provided to help understanding of the present invention, but the present invention is not limited thereto. In addition, the technical features related to the embodiments of the present invention described below may be combined with each other as long as they do not conflict with each other.

A gas supplementing system of a heat pump all-in-one machine is shown in figure 1 and comprises a compressor 1, a three-pipe control liquid storage device 4, a first heat exchanger, a second heat exchanger, a four-way reversing valve 2, a one-way valve 81, a first expansion valve, a second expansion valve, a first temperature sensor 71 and a second temperature sensor 72.

The utility model discloses an in the embodiment, compressor 1 is jet enthalpy increasing compressor 1 (EVI compressor 1), and EVI compressor 1 is provided with three connector: exhaust port, suction port and air supplement port.

The four-way reversing valve 2 comprises a first valve port, a second valve port, a third valve port and a fourth valve port, the first valve port is connected with an exhaust port of the EVI compressor 1 through a first pipeline 61, the second valve port is connected with a first heat exchanger through a second pipeline 62, the third valve port is connected with a second heat exchanger through a third pipeline 63, and the fourth valve port is connected with an air suction port of the EVI compressor 1 through a fourth pipeline 64; when the system heats, the first valve port is communicated with the second valve port, the third valve port is communicated with the fourth valve port, and when the system cools, the first valve port is communicated with the third valve port, and the second valve port is communicated with the fourth valve port.

In the embodiment of the present invention, a check valve 81 is further provided on the first pipe 61 connecting the first valve port and the exhaust port of the EVI compressor 1.

In addition, in order to protect the system to prevent that excessive pressure from causing the system to damage or causing other dangers, still be provided with pressure switch 93 on first pipeline 61, when the system surpassed predetermined pressure value, pressure switch 93 self-closing system in the embodiment of the utility model, predetermined pressure value can be 3.9MPa.

The first pipeline 61 is further provided with a first pressure sensor 91 and a third temperature sensor 73, the third temperature sensor 73 is used for detecting the temperature value of the first pipeline 61 in real time, the first pressure sensor 91 is used for detecting the pressure value on the first pipeline 61 and calculating to obtain the saturation temperature, and the superheat degree is obtained through the real-time temperature value of the first pipeline 61 detected by the third temperature sensor 73 and the saturation temperature converted by the first pressure sensor 91.

The fourth pipeline 64 is further provided with a second pressure sensor 92 and a fourth temperature sensor 74, and the pressure sensor and the temperature sensor acting on the first pipeline 61 of the second pressure sensor 92 and the fourth temperature sensor 74 have similar functions and are not described again.

The utility model discloses an in the embodiment, first heat exchanger is water heat exchanger 3, and the second heat exchanger is wind heat exchanger 5.

The utility model discloses an in the embodiment, three control reservoir 4 include first exchange port, second exchange port and gas outlet, and the liquid in three control reservoir 4 passes through first exchange port and the business turn over of second exchange port, and the gas in three control reservoir 4 passes through the gas outlet business turn over.

Specifically, the air outlet is connected with an air supplement port of the EVI compressor 1 through a fifth pipeline 65, the first exchange port is connected with the first heat exchanger through a sixth pipeline 66, the second exchange port is connected with the second heat exchanger through a seventh pipeline 67, the fifth pipeline 65 is provided with a first temperature sensor 71, the sixth pipeline 66 is provided with a first electronic expansion valve 82 and a second temperature sensor 72, and the seventh pipeline 67 is provided with a second electronic expansion valve 83.

In addition, a solenoid valve 84 is provided in the fifth line 65 in order to protect the lines and to protect the system when the overpressure or the degree of superheat of the make-up gas is insufficient.

The utility model discloses a heat pump all-in-one system includes two mode: heating circulation mode and refrigeration circulation mode, specifically:

heating cycle mode: high-temperature and high-pressure gas in the EVI compressor 1 enters the check valve 81 from the exhaust port through the first pipeline 61 and then enters the four-way reversing valve 2, at the moment, the temperature of the gas in the first pipeline 61 is about 50-100 ℃, the saturation temperature is about 40-60 ℃, and the pressure is about 2.3-3.8 MPa; then, the refrigerant enters the hydrothermal exchanger 3 from a second valve port of the four-way reversing valve 2 through the second pipeline 62, after heat exchange is carried out with water in the hydrothermal exchanger 3, the temperature and the pressure of the condensed refrigerant are both slightly reduced, the refrigerant is throttled to the intermediate pressure from the sixth pipeline 66 through the first electronic expansion valve 82 and then enters the three-pipe liquid storage device 4, and the temperature of the refrigerant after the first electronic expansion is at least 5 ℃ lower than the saturation temperature of the first pipeline 61; the refrigerant entering the three-pipe liquid storage device 4 is partially gasified and absorbs heat, then enters the EVI compressor 1 from the fifth pipeline 65 through the electromagnetic valve 84, the other part of the refrigerant is subcooled, throttled and depressurized from the seventh pipeline 67 through the second electronic expansion valve 83, enters the wind heat exchanger 5 for evaporation and heat absorption, and then enters the EVI compressor 1 from the third pipeline 63 through the four-way reversing valve 2 and the fourth pipeline 64.

Refrigeration cycle mode: high-temperature and high-pressure gas in the EVI compressor 1 enters the one-way valve 81 from the exhaust port through the first pipeline 61 and then enters the four-way reversing valve 2; then, the refrigerant enters the wind heat exchanger 5 from a third valve port of the four-way reversing valve 2 through a third pipeline 63, the condensed liquid refrigerant after exchanging heat with air in the wind heat exchanger 5 is throttled to an intermediate pressure from a seventh pipeline 67 through a second electronic expansion valve 83 and then enters a three-pipe liquid storage device 4, and part of the refrigerant is gasified to absorb heat and then enters the EVI compressor 1 from a fifth pipeline 65 through an electromagnetic valve 84; the other part of the refrigerant enters the first electronic expansion valve 82 from the sixth pipeline 66 after being cooled, enters the hydrothermal exchanger 3 after being throttled and depressurized, evaporates and absorbs heat, enters the four-way reversing valve 2 from the second pipeline 62, enters the EVI compressor 1 from the fourth pipeline 64, and in the process, the temperature of the gas in the fourth pipeline 64 is about-23-36 ℃, the saturation temperature is about-25-11 ℃, and the pressure is about 0.15-1 MPa.

The state of the unit after shutdown can be optimized by the check valve 81: when the unit is stopped in a cooling operation, the second electronic expansion valve 83 is immediately closed, so that the part between the check valve 81 and the second electronic expansion valve 83 can be always kept in a high-pressure state, the energy loss caused by entropy increase due to the mixing of refrigerants at high and low pressure sides is avoided, and meanwhile, the refrigerant in the pipeline between the check valve 81 and the EVI compressor 1 can leak to the low pressure side through the EVI compressor 1, so that the pressure can be quickly balanced, and the condition of loaded starting of the compressor cannot be caused.

The heating operation stop principle is similar to the cooling operation stop principle, and is not described in detail.

The opening degree of the first electronic expansion valve 82 and the second electronic expansion valve 83 can be adjusted to control the air supplement amount, the opening degree of the first electronic expansion valve 82 can be controlled by the air supplement temperature (namely the temperature monitored by the first temperature sensor 71) and the temperature difference between the temperature of the first electronic expansion valve 82 after throttling, the temperature difference superheat degree of 1 ℃ can be generally selected, when the air supplement superheat degree is lower than the 1 ℃ air supplement superheat degree required by the system, the electromagnetic valve 84 on the fifth pipeline 65 is controlled to be closed, air supplement is not performed on the EVI compressor 1 any more, the running reliability of the EVI compressor 1 is ensured, at the moment, the three-pipe liquid reservoir 4 only plays a role of a liquid reservoir, and the refrigerant system is equivalent to a common refrigerant system without air supplement; the opening degree of the second electronic expansion valve 83 can be controlled by conventional suction superheat and will not be described in detail.

The high pressure and the low pressure are separated in the two systems after the unit of the system is shut down, thereby avoiding the capacity loss caused by the mixing of the refrigerants at the high pressure side and the low pressure side, leading the unit not to lose too much capacity when frequently starting and stopping under the low-load working condition, and simultaneously leading the unit to refrigerate and heat more rapidly when starting again after the unit is shut down to the warm temperature because the system keeps the high pressure and the low pressure all the time; compared with the traditional mode of carrying out high-low pressure balance by switching the four-way valve, the design can avoid noise caused by high-low pressure switching of the four-way valve, and improve the comfort level of a user; due to the adoption of the design, the refrigerant is always kept at the high-pressure side when the compressor is stopped, the migration of the stopped refrigerant from the high-pressure side to the low-pressure side is avoided, the liquid return phenomenon when the compressor is started next time can be reduced, the starting power and the current of the compressor are reduced, and the operation of the whole heat pump unit is more reliable.

The embodiments of the present invention have been described in detail with reference to the accompanying drawings, but the present invention is not limited to the described embodiments. It will be apparent to those skilled in the art that various changes, modifications, substitutions and alterations can be made in the embodiments without departing from the principles and spirit of the invention, and these embodiments are still within the scope of the invention.

Claims

1. The utility model provides a heat pump all-in-one tonifying qi system which characterized in that includes:

a compressor including an exhaust port, an intake port, and a supply port;

a check valve disposed on the first line; and

the liquid in the three-control liquid storage device enters and exits through the first exchange port and the second exchange port, and the gas in the three-control liquid storage device enters and exits through the gas outlet;

2. The air supplementing system of the heat pump all-in-one machine as claimed in claim 1, wherein a control valve is further arranged on the fifth pipeline.

3. The air supplementing system of the heat pump all-in-one machine as claimed in claim 2, characterized in that: the first expansion valve and the second expansion valve are both electronic expansion valves.

4. The air supplementing system of the heat pump all-in-one machine as claimed in claim 3, characterized in that: the control valve is an electromagnetic valve.

5. The air supplementing system for the heat pump all-in-one machine of claim 4, characterized in that: the compressor is an enhanced vapor injection compressor.